Method for controlling the power consumption of a hydrodynamic clutch by controlling the volumetric efficiency and a hydrodynamic clutch

ABSTRACT

The invention relates to a method for controlling the power consumption of a starting element ( 1 ) in the form of a hydrodynamic clutch ( 2 ). Said clutch comprises an impeller ( 4 ) and a turbine wheel ( 5 ), which together form at least one toroidal working chamber ( 6 ) that can be filled with an operating medium, and is located in a drive train ( 3 ) with at least one other drive motor that can be coupled to the hydrodynamic clutch. The method is characterized in that the power consumption can be freely adjusted as a function of the volumetric efficiency of the hydrodynamic clutch and said method has the following characteristics: the supply or evacuation of the operating medium to or from the working chamber is influenced by the generation and introduction of a static superposition pressure in the closed rotating circuit; the operating medium is supplied or evacuated to or from the working chamber by the application of a superposition or influencing pressure to the operating medium level in the operating medium reservoir ( 40 ).

[0001] The invention relates to a method for controlling the power consumption of a hydrodynamic clutch, in particular as starting element in a drive train by controlling the volumetric efficiency, in detail with the features from the generic term of claim 1; furthermore a hydrodynamic clutch, a use of the same and a use of the method.

[0002] During the starting process, i.e. the run-up of the drive motor and simultaneous transmission of torque on the output unit in a drive train, in particular in vehicles but also in stationary units, the problem of the energy consumption of the drive motor is increasingly the center of attention since during this process usually too little energy for the self-acceleration of the drive motor is available. As starting elements in vehicles hydrodynamic clutches are used for this process among other things. They are well-known in a multiplicity of designs. Herewith it is referred to the printed matter Voith: “Hydrodynamics in motive power engineering”, Vereinigte Fachverlage, Krauskopf Engineer Digest, Mainz 1987. Thereby the starting elements are usually integrated in a gear box unit. The gear box unit exhibits for this a first hydrodynamic transmission part and a further second transmission part, which is usually preferably formed by a mechanical transmission part for the application in vehicles. Since the power consumption of the hydrodynamic clutch is dependent on its design and not on a machine, which is at least indirectly connected to the hydrodynamic clutch on the output side, during the installation of such a component between a drive motor and a machine it is to be considered that for each load condition between the machine and the hydrodynamic clutch also a state of equilibrium must be ensured between the drive motor and the hydrodynamic component. Thereby the power released by the drive motor is in the rarest case completely available to the gear construction unit, in particular the hydrodynamic component, during the starting process. Power for auxiliary machines, like for example fans, generators, pumps and so on, which are arranged before the starting element respectively the gear inlet, must thereby be subtracted from the available drive power. For the use of a hydrodynamic component in form of a hydrodynamic clutch the following specified benefits of the hydrodynamic power transmission are thereby substantial for the starting process: wear-free as well as vibration reducing and thermally stable. In connection with drive motors for different application functions thereby concrete demands are made regarding the transfer characteristic also during the starting process. In particular for the application in vehicles a certain behavior during the starting process, in particular a certain power consumption by the impeller of the hydrodynamic clutch, is desired in order to be able to drive the drive motor in an optimized operating range regarding a certain parameter. During the starting process at low speeds it is therefore required that a suitable surplus moment is present for the self-acceleration of the drive motor in order to realize a motor start-up that is relieved as much as possible.

[0003] It is therefore the task of the invention, to further develop a starting unit of the kind initially specified, in particular a method for controlling the power consumption, in such a manner that said starting units are suitable in particular for the application in drive trains of vehicles or other ranges of application, whereby besides the advantages of the hydrodynamic power transmission also a substantially relieved start-up of the drive motor should be ensured. The design of the starting unit should be characterized by a low expenditure for design, production and control and it should be economical. Furthermore the solution according to the invention, independently of the field of application at the hydrodynamic component, is to require only slight modifications.

[0004] The solution according to the invention is characterized by the features of claims 1 and 10. Favorable embodiments are described in the sub-claims. Favorable areas of application are described in the application claims.

[0005] According to the invention the power consumption as a function of its volumetric efficiency is freely adjustable with a method for controlling the power consumption of a starting element in form of a hydrodynamic clutch, comprising an impeller and a turbine wheel, which form with one another at least one toroidal working chamber that can be filled with operating medium, in a drive train with at least another drive motor that can be coupled with the hydrodynamic clutch. This possibility of free adjusting makes it possible, regarding different criteria, for example energy consumption and pollutant emission, to try to achieve optimized operating points in the characteristic diagram of the drive motor.

[0006] Thereby a change of the power to be received takes place by controlling the volumetric efficiency of the hydrodynamic clutch when a value is present, which characterizes the power desired to be received of the hydrodynamic clutch at least indirectly. The controlling of the volumetric efficiency takes thereby place preferably via creating and/or applying of an influence pressure on a resting medium, in particular on an operating medium level which arises in an operating medium reservoir within the scope of an operating medium utility system or on a control medium level. Thereby a portion of the operating medium in the working chamber is directed during the operation of the hydrodynamic clutch in a closed circuit between at least one outlet from the toroidal working chamber between impeller and turbine wheel and at least one inlet into the toroidal working chamber, whereby the inlet is connected with an operating medium reservoir which is pressure tight closed in relation to its surrounding. A manipulated variable is then created for the generation of an influence pressure on the medium resting in the operating medium reservoir and the servo unit is triggered. Filling or emptying takes place up to the point of reaching a pressure balance between the operating medium level in the operating medium reservoir and the rotary closed circuit.

[0007] The embodiment of the hydrodynamic clutch according to the arrangement is described in claim 10.

[0008] A hydrodynamic clutch according to the invention comprises at least two rotating circuit parts in form of two impellers, which form with one another at least one toroidal working chamber, which can be filled with operating medium and in which a rotary working circuit arises during operation of the hydrodynamic clutch. An inlet and an outlet are assigned to the toroidal working chamber, which is connected with a closed circuit. Said working chamber comprises the working circuit and an external element, i.e. an element directed outside of the toroidal working chamber, which is connected with the working circuit. The external element of the circuit serves thereby among other things the purpose of directing the operating medium for the purpose of cooling. This closed circuit is designed according to the invention pressure tight. This means in detail, that the inlet, in particular the inlet area to the working chamber and the outlet, in particular the outlet area are designed tight in relation to the hydrodynamic clutch and that further the operating medium guide distance between the inlet and the outlet is completely sealed in the external element of the closed circuit, i.e. outside of the toroidal working chamber.

[0009] The solution according to the invention makes it possible that during operation of the hydrodynamic clutch operating medium is directed in the external element of the circuit with removal of operating medium from the working circuit into the external element of the closed circuit and, since the whole circuit is designed as a closed circuit, operating medium is again supplied to the inlet. Due to the pressure tight design a pressure in the closed system, created by the hydrodynamic clutch, is maintained during the operation of the hydrodynamic clutch, i.e. during rotation of an impeller and therefore by slaving at least another impeller by means of the working circuit. This circuit can be designated thereby by itself as cooling circuit, as heat can be dissipated by radiant heat over the line connections between the outlet and the inlet. Therefore already this design makes a cooling circuit possible.

[0010] If under a further aspect means for the generation of an influence pressure on the operating medium directed in the closed circuit are planned, the possibility consists to control additionally the volumetric efficiency of the hydrodynamic clutch.

[0011] Under a further aspect at least one knot location for the optional connection of means for the filling and/or emptying and/or means for the pressure default are arranged in the system in the closed circuit. The means for the pressure default are thereby preferably pressure tight connected to the closed circuit and serve the purpose to generate a static superposition pressure in the closed circuit. The means for the pressure default comprise preferably a pressure tight closed reservoir, which is pressure tight connected with the closed circuit. The pressure default takes place thereby via applying a pressure on the reservoir level. Another possibility consists in the generation of a pressure through additional components, for example a suitable pump device.

[0012] The means for filling comprise an operating medium reservoir device and a means for the operating medium transport, for example pump devices. These serve also the purpose of loss compensation.

[0013] Under a further aspect of the invention the means for filling and emptying and the means for the pressure default are formed by a system for the purpose of the simplification of the overall system. Filling and emptying takes thereby place preferably likewise by means of the reservoir, which is connected pressure tight to the closed system, and by applying pressure on the reservoir level or by pump devices.

[0014] An improvement of the invention contains the provision and/or the allocation of standing back pressure tubes to the diverting area, which is limited by a rotating housing component. Preferably a multiplicity of standing back pressure tubes is intended, which are arranged in a certain distance to each other in circumferential direction. The back pressure tubes function as back pressure pump device when immersing into the diverting area and are connected with the line connections, which are connected with the diverting area. These convert thereby the kinetic energy into pressure energy and create so automatically a cooling circuit, which is required for ensuring the continuous operation of the hydrodynamic clutch. In a further design of the solution according to the invention means for the heat dissipation in the closed circuit are intended. These can be executed thereby as cooling devices or heat exchangers.

[0015] The hydrodynamic clutch designed as starting element according to the invention is not limited to a concrete application regarding its application ranges in drive trains. Application can take place in drive trains of stationary units or mobile devices, preferably in a vehicle.

[0016] The solution according to the invention is in the following described using figures. The following is detailed represented:

[0017]FIG. 1 illustrates a favorable design of a starting element in form of a turbo-clutch arranged according to the invention using a section of a drive train;

[0018]FIG. 2 illustrates the basic principle of the controlling of the volumetric efficiency using a diagrammatic representation of a hydrodynamic clutch and the operating medium utility system assigned to said clutch.

[0019]FIG. 1 illustrates a favorable design of a starting element 1 in form of a hydrodynamic clutch 2 arranged according to the invention, in particular a turbo-clutch using a section of a drive train 3. The hydrodynamic clutch 2, in particular turbo-clutch comprises at least one primary wheel functioning as impeller 4 and a secondary wheel functioning as turbine wheel 5, which form with one another a toroidal working chamber 6. The starting element 1 comprises further one drive unit 7, that can be coupled at least indirectly with a drive motor here not represented, and one output unit 8 that can be coupled at least indirectly with the output unit at the drive system, i.e. indirectly via further transmission means or directly without inserting further transmission means. The output unit 8 can thereby generally be coupled with a mechanical speed and/or torque transformer during the application in gear boxes. The drive unit 7 and the output unit 8 are thereby formed for example in each case by a shaft or a hollow shaft or a flange. The hydrodynamic clutch 2 exhibits further a housing 9, which is connected secured against torsion with the impeller 4 and consists because of assembly reasons preferably of a multiplicity of individual housing components 25.1-25.3. The housing 9 is therefore likewise connected secured against torsion with the drive unit 7. In the represented case the housing 9 is therefore connected with a hub component 10, which is designed flange-like at its end range 11 facing the starting element, whereby the mounting respectively the realization of the connection secured against torsion between the hub component 10 and the housing 9 takes place in the area of a flange 12 at the hub component 10. The drive of the hub component 10 takes place through a drive shaft 13, which can be connected at least indirectly, i.e. either directly or over further power transmission components with a drive motor not represented here, and through a suitable shaft-hub connection 14 which in the represented case is designed as key joint 15 between hub component 10 and drive shaft 13. Other design variations for the realization of a connection secured against torsion are likewise conceivable. The housing 9 encloses the turbine wheel 5 while forming a first gap 16 in axial direction. The first gap 16 is thereby limited by a housing inner wall 17 of a housing component 25.1, by an outlet 18 from the impeller 4 in the range of the parting plane 19 between impeller 4 and turbine wheel 5, by the outer circumference 20 in the range of radially outer extension 21 of the turbine wheel 5, and by a further housing component 25.2, which is connected secured against torsion directly with the impeller 4 or which forms a structural unit with the impeller, in particular its inner surface 31. Means 22 are intended for sealing the gap 16 between the housing 9 and the turbine wheel 5. These means for sealing 22 comprise at least one non-contact sealing device 23, which is designed preferably in form of a labyrinth seal. The housing 9 forms further a second gap 28 with the impeller 4 and a further housing component 25.3, connected secured against torsion the impeller, as well as a second housing 51 with rotates with relative speed in relation to the housing 9, is preferably however resting, which is mounted via an arrangement of bearings 26 on a driven shaft 27 which forms the output unit 8 of the starting element 1. This second gap is essentially formed for by the outer surface 29 of the impeller 4 in the radially outer range 30, by the housing component 25.2, which carries the housing inner wall 31, and by an inner surface 33 of the housing component 25.3 of the housing 9, which at least partially encloses the impeller 4 in axial direction. The resting housing 51 can be designed as one-piece or however as multiple pieces. It can also rotate—depending on the connection to the output unit 8—with relative speed in relation to the rotation of the housing 9. A seal between the housing component 25.3 and a housing component 51.1 of the resting housing 51, into which line connections 41 for the realization of a closed operating medium circuit 42 are integrated, is created by means 34 for sealing the gap 28 between the housing 9 and the housing 51, in particular the housing components 25.3 and 51.1. These means comprise at least a non-contact gasket 35, which is designed preferably in form of a labyrinth seal. The second gap 28 is connected at the housing component 25.2 with the first gap 16 via suitable transfer ports 36 in the housing wall 32. Means 37 for the removal of operating medium, which appears in the second gap 28 during the operation of the hydrodynamic clutch via the operating medium guide in the toroidal working chamber 6, are assigned to the second gap 28, said means being designed for example in the form of back pressure pumps 38. According to the desired amount of operating medium to be removed from the second gap 28 and the time period, which is available for the removal, preferably in dependence of the possible passage area, which is determined by the dimensioning of the back pressure pumps 38, a multiplicity of back pressure pumps 38 is intended, which are preferably arranged in symmetrical distances in circumferential direction in the gap 28 respectively immerse into the gap. The housing components 51.1 and 51.2 and the third housing component 25.3 form thereby a back pressure pump housing 54, the housing component 25.3 for itself alone the impeller shell 52. The housing components 51.1 and 51.2 can also be designed as integral unit, i.e. only one housing component is intended, which combines the housing components 51.1 and 51.2 represented in the figure in itself. The means for the removal 37, in particular the back pressure pumps 38, are thereby connected with means 39 for the direction of operating medium in a closed circuit 42. The means 39 for directing the operating medium comprise therefore preferably line connections 41 in the form of operating medium channels 50, which are integrated into the housing wall facing the impeller 4 respectively into the housing components 51.1 and 51.2 of the housing 51. The rotating housing 25 and the housing 51, which is either resting or rotating with relative speed to the housing 25, form the total housing 55 for the clutch 2. The operating medium utility system 53 comprises an operating medium reservoir 40, which is connected with the closed circuit 42 via a knot location 56, for example by means of a line connection. The operating medium reservoir 40 is preferably arranged in the area below the height of the toroidal working chamber 6, in particular within the outer radial dimensions of the individual impellers 4 or 5 in assembly position. In this case a safety device via a siphon or other aids can be omitted.

[0020] The operating medium reservoir 40 is thereby pressure tight connected with the inlet 44 into the toroidal working chamber 6 via the knot location 56. The means for sealing 34 of the gap 28, in particular of the back pressure pump housing 54 and the impeller shell 52, as well as the means 22 for sealing between turbine wheel 5 and the rotating housing 9 of the starting unit 1 are spatially arranged in circumferential direction above the meridian center and below the maximum profile diameter of the two impellers, i.e. the impeller 4 and the turbine wheel 5. Furthermore means are intended for sealing 43 between impeller 4 and turbine wheel 5, whereby these means are arranged in radial direction below the internal diameter d_(E) of the toroidal working chamber 6. The closed circuit 42 is thus pressure tight in relation to its surrounding. The connection of the operating medium reservoir 40 to the closed circuit 42 takes place likewise pressure tight.

[0021] The housing of the starting unit 9, the impeller 4, the turbine wheel 5, the closed circuit 42 as well as the pressure tight connection of the operating medium reservoir 40 with the closed circuit 42 form means 45 for the generation of a pressure balance between a closed rotating circuit 42 and a resting medium. The closed circuit 42 is realized between the outlet 18 from the toroidal working chamber 6 in the area of the parting plane 19 and the inlet 44 into the impeller 4. The operating medium arrives from the flow circuit in the toroidal working chamber 6 via the outlets 18 in the area of the parting plane 19 of the impeller 4 and the turbine wheel 5 and via the connection channels into the second gap 28, from where the operating medium is directed via the means for the removal 37, in particular the back pressure pumps 38, into the closed circuit 42.

[0022] The inlet 44 is via the filling location 47 connected with the operating medium reservoir 40. In a particularly favorable design the filling location 47 is furthermore designed as bladed channel 48. This means that direction components 49, which extend in the direction of the flow toward the toroidal working chamber 6, are intended. The reduction of the operating medium stream via the outside impeller shell 52, formed by the housing component 25.3, takes preferably place via a multiplicity of stationary back pressure pumps 38, which are arranged to each other in circumferential direction preferably in symmetrical distance. The circuit created for cooling purposes is thereby designed as closed circuit 42.

[0023] The working principle of the filling control by means of an outside pressure onto a resting medium is described in diagrammatic simplified representation in FIG. 2. This figure illustrates in diagrammatic simplified representation a hydrodynamic clutch 2, the closed circuit 42 assigned to said clutch, which is designed as coolant circle, and the connection between the turbo-clutch 2 and the operating medium reservoir 40. The operating medium reservoir 40 is thereby for example designed as tank or vessel, whereby it can also be formed by the housing of the starting unit or of the gear box, in which the starting element 1 is arranged. The operating medium reservoir 40 is thereby preferably arranged below the internal diameter d_(E) of the toroidal working chamber 6. It is thereby crucial that the operating medium level is either below this dimension or it can be above, with the presence of suitable aids, for example in the form of siphons and/or valves. The closed coolant circuit 42 is designed between the toroidal working chamber 6 respectively the outlet 18 from the toroidal working chamber 6 and the filling location 47 of the toroidal working chamber 6. Means for the heat dissipation of operating medium 57 are for example arranged in said circuit. These means 57 comprise in the simplest case for example a heat exchanger or a cooling device. Directing the operating medium from the working chamber 6 into the working chamber 6 in the closed circuit 42 serves thereby mainly the purpose of cooling the operating medium, in particular the generation of a continuous cooling operating medium flow. The operating medium utility system comprises a pressure tight designed operating medium reservoir 40, for example in form of an operating medium sump in a reservoir, a tank or a housing, which can be connected via at least one connection channel with the closed circuit 42 in the area of the inlet 44. The operating medium reservoir 40 is thereby preferably arranged in such a manner that the arising operating medium level is arranged underneath the toroidal working chamber 7. An influence pressure p_(B) for the change of the volumetric efficiency FG is applied on the operating medium level, whereby said influence pressure during effect on the closed sump allows operating medium to enter the working circuit in the toroidal working chamber via connection channels, until the pressure within the area of the inlet 21 after the heat exchanger creates a pressure balance. Filling or emptying takes place until a pressure balance between the operating medium level in the operating medium reservoir and the rotary closed circuit arises.

[0024] Furthermore the profiles of the turbine wheel 5 and the impeller 4 are offset in radial direction against each other by a certain value a in such a manner that the outside profile diameter of the turbine wheel 5 exhibits a larger dimension in radial direction than the outside profile diameter of the impeller 4 and the interior profile diameter of the turbine wheel 5 exhibits likewise a larger dimension than the internal diameter of the impeller profile.

[0025] A change of the ideal torus-symmetrical form can take place moreover via a profile offset.

[0026] The back pressure pumps 38 supply with emptied turbo-clutch 2, when all circuit parts are free of operating medium, a flow rate and an oil pressure for cooling or for actuation for other consumers, like for example a wet-running mechanical clutch.

[0027] Further favorable designs consist of the fact that means for the improvement of the filling of the working chamber, i.e. the pump characteristic, is intended by things built into the filling area 48 connected with the filling location 47. These things built in can be designed as filling blades 49, perforated plate packages or similarly designed parts. Furthermore it is conceivable to design the filling of the impeller 4 through several blade cascades in arbitrary parts of the torus or through the blade itself for example a stamped channel to the torus center.

[0028] Further improvements can consist of the fact that the blades of impeller 4 and turbine wheel 5 are designed with different blade angles. Additionally or as individual solution the blades of impeller 4 and turbine wheel 5 can be sharpened differently, which entails into different dimensions across the extension in circumferential direction of the individual blade. Another possibility consists of changing the entry angles and outlet angles between impeller and turbine wheel or to intend a different number of blades in the mounting of blades of impeller 4 and turbine wheel 5.

[0029] Reference Symbol List

[0030]1 Starting element

[0031]2 Turbo-clutch

[0032]3 Drive train

[0033]4 Impeller

[0034]5 Turbine wheel

[0035]6 Toroidal working chamber

[0036]7 Drive unit

[0037]8 Output unit

[0038]9 Housing

[0039]10 Hub component

[0040]11 End range facing the starting element

[0041]12 Flange

[0042]13 Drive shaft

[0043]14 Shaft-hub connection

[0044]15 Key joint

[0045]16 Gap

[0046]16 Housing inner wall

[0047]17 Outlet

[0048]18 Parting plane

[0049]19 Outer circumference

[0050]20 Radially outer extension

[0051]21 Means for sealing

[0052]22 non-contact sealing device

[0053]25.1, 25.2,

[0054]25.3 Housing component

[0055]26 Arrangement of bearings

[0056]27 Driven shaft

[0057]28 Gap

[0058]29 Outer surface

[0059]30 radially outer range

[0060]31 Inner surface

[0061]32 Housing wall

[0062]33 Inner surface

[0063]34 Means for sealing the gap 28

[0064]35 Non-contact gasket

[0065]36 Transfer port

[0066]37 Means for the removal of operating medium from the working chamber

[0067]38 Back pressure pump

[0068]39 Means for directing the operating medium

[0069]40 Operating medium reservoir

[0070]41 Line connections

[0071]42 Closed circuit

[0072]43 Means for sealing between impeller and turbine wheel

[0073]44 Inlet

[0074]45 Means for the generation of a pressure balance between a closed rotating circuit and a round medium

[0075]47 Filling location

[0076]48 Filling area

[0077]49 Bladed direction components

[0078]50 Operating medium channels

[0079]51 Resting housing component

[0080]52 Impeller shell

[0081]53 Operating medium utility system

[0082]54 Back pressure pump housing

[0083]55 Total housing

[0084]56 Knot location

[0085]57 Means for heat dissipation

[0086] d_(E) Inner diameter of the toroidal working chamber 

1. Method for controlling the power consumption of a starting element (1) in form of a hydrodynamic clutch (2), comprising an impeller (4) and a turbine wheel (5), which form with one another at least one toroidal working chamber that can be filled with an operating medium (6), and is located in a drive train (3) with at least one other drive motor that can be coupled to the hydrodynamic clutch (2), thereby characterized that the power consumption can be freely adjusted as a function of the volumetric efficiency of the hydrodynamic clutch (2), characterized by the following features: 1.1. at least one portion of the operating medium in the working chamber (6) is directed during the operation of the hydrodynamic clutch (2) in a closed rotating circuit (42) between at least one outlet (18) from the toroidal working chamber (6) between impeller (4) and turbine wheel (5) and at least one inlet (44) into the toroidal working chamber (6); 1.2. the supply of operating medium to the working chamber (6) or the removal of operating medium from the working chamber (6) is influenced by the generation and introduction of a static superposition pressure into the closed rotating circuit. 1.3. the operating medium can be supplied to or removed from the working chamber (6) via a operating medium reservoir (40) which is pressure tight connected to the inlet (44) in the toroidal working chamber (6); 1.4. and the supply of operating medium to the working chamber (6) removal or the removal of operating medium from the working chamber (6) takes place by applying a superposition pressure respectively an influence pressure to the operating medium level of the operating medium reservoir (40).
 2. Method according to claim 1, characterized by the fact that a value is present, which characterizes the power desired to be received of the hydrodynamic clutch (2) at least indirectly, said value controlling the volumetric efficiency of the hydrodynamic clutch (2) in order to change of the power to be received.
 3. Method according to claim 1 or 2, characterized by the fact that when a value is present, which characterizes the power desired to be received of the hydrodynamic clutch (2) at least indirectly, a manipulated variable is created for the generation of an influence pressure on the operating medium resting in the operating medium reservoir (40), and a servo unit intended for the generation of the influence pressure is triggered.
 4. Method according to claim 3, characterized by the fact that the duration of the filling or emptying process is characterized by the length of time for the adjustment of a pressure balance between the operating mediums present in the operating medium reservoir (40) and the rotary closed circuit (42) of the operating medium.
 5. Method according to one of the claims 3 or 4, characterized by the fact that the filling and/or emptying of a complete filling are accomplished in a time period of equal or smaller than 1s.
 6. Method according to one of the claims 3 to 5, characterized by the fact that the influence pressure can be controlled in dependence of at least one of the parameters following specified: speed of the impeller; value of the torque at the impeller; value of the torque at the turbine wheel, speed of the turbine wheel.
 7. Method according to one of the claims 3 to 6, characterized by the fact that the value of the component current of the operating medium present during the operation of the hydrodynamic clutch (2) in the working chamber (6), which is directed in a closed circuit (42) between at least one outlet (18) from the toroidal working chamber (6) between impeller (4) and turbine wheel (5) and at least one inlet (44) into the toroidal working chamber (6), is controlled independently of an effect on the power consumption in dependence of the temperature in the working circuit in the toroidal working chamber (6).
 8. Hydrodynamic clutch (2) 8.1. with an impeller (4) and a turbine wheel (5), which form with one another at least one toroidal working chamber (6); 8.2. with means for directing the operating medium in a closed circuit of at least one outlet (18) from the toroidal working chamber (6) into at least one inlet (44) of the toroidal working chamber (6); 8.3. the closed circuit (42) is designed pressure tight. 8.4. with a knot location (56) in the closed circuit (42); 8.5. with means for the optional connection of means for the filling and/or emptying and/or means for the influence of the pressure of the operating medium which is directed in the closed circuit (42) to the knot location (56).
 9. Hydrodynamic clutch (2) according to claim 8, characterized by the following features: 9.1. with an operating medium utility system (53), comprising an operating medium reservoir (40), connected with the inlet (44) into the toroidal working chamber (6); 9.2. with means for a pressure tight connection between the operating medium reservoir (40) and the inlets (44).
 10. Hydrodynamic clutch (2) according to one of the claims 8 to 9, characterized by the following features: 10.1. with a housing (9) which is connected secured against torsion with the impeller (4); 10.2. the housing (9) encloses the turbine wheel (5) in axial direction while forming a first gap (16); 10.3. the first gap (16) is moreover limited by the outer circumference of the turbine wheel (5), whereby a non-contact sealing device (23) is intended between housing (9) and turbine wheel (5); 10.4. the housing (9) forms a further second gap (28) with a resting housing component (51), into which means (37) submerge for the removal of operating medium from the impeller shell (52).
 11. Hydrodynamic clutch according to claim 10, characterized by the fact that the means (37) for the removal of operating medium comprise at least one stationary back pressure pump device (38).
 12. Hydrodynamic clutch (2) according to one of the claims 10 or 11, characterized by the following features: 12.1. with means for sealing the second gap (28) between the housing (9) and the round housing component (51); 12.2. with means (43) for sealing between the impeller (4) and the turbine wheel (5) below the inside diameter (d_(E)) of the toroidal working chamber (6).
 13. Hydrodynamic clutch (2) according to one of the claims 8 to 12, characterized by the following features: 13.1. the inlet (44) is connected with a filling area (48) via a filling location (47); 13.2. the filling location (47) is designed as bladed channel (48) comprising direction components (49).
 14. Hydrodynamic clutch (2) according to claim 13, characterized by the fact that the direction components (49) extend in the direction of the flow toward the toroidal working chamber (6).
 15. Hydrodynamic clutch (2) according to one of the claims 8 to 14, characterized by the fact that the profiles of the turbine wheel (5) and the impeller (4) are offset by a certain value (a) in radial direction.
 16. Hydrodynamic clutch (2) according to claim 15, characterized by the fact that the outside profile diameter of the turbine wheel (5) exhibits in radial direction a larger dimension than the outside profile diameter of the impeller (4) and that the interior profile diameter of the turbine wheel (5) exhibits a larger dimension than the interior profile diameter of the impeller.
 17. Hydrodynamic clutch (2) according to one of the claims 8 to 16, characterized by the fact that the inlet (44) into the toroidal working chamber (6) is intended at the impeller (4).
 18. Hydrodynamic clutch (2) according to one of the claims 8 to 16, characterized by the fact that the inlet (44) into the toroidal working chamber (6) is arranged at the turbine wheel (5).
 19. Hydrodynamic clutch (2) according to one of the claims 17 or 18, characterized by the fact that the inlet (44) into the toroidal working chamber takes place via the blades.
 20. Hydrodynamic clutch (2) according to one of the claims 17 to 19, characterized by the fact that the filling of the toroidal working chamber (6) takes place in the area of the statically lowest pressure into the working chamber (6).
 21. Use of a method in accordance with one of the claims 1 to 7 for the speed regulation of a drive motor in a drive train that can be coupled with the hydrodynamic clutch.
 22. Use of a hydrodynamic clutch in accordance with one of the claims 8 to 20 in a drive train with a drive motor in form of a combustion engine.
 23. Use of a hydrodynamic clutch in accordance with one of the claims 8 to 20 in a drive train with a drive motor in form of an electric motor.
 24. Use in accordance with one of the claims 22 or 23 in a vehicle.
 25. Use in accordance with one of the claims 25 or 26 in a stationary unit. 